JPS60213666A - Winding machine - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

[Detailed description of the invention] <Industrial application field> The present invention relates to winding yarn into packages.

As used herein, the term "thread" includes all thread-like structures, such as wires, yarns of all types, glass fiber strands, etc.

The present invention preferably contemplates the winding of synthetic plastic filament yarns, including either monofilaments or multifilaments, but is not limited thereto.

BACKGROUND OF THE INVENTION In the current standard practice, synthetic plastic filaments are carried in the chuck of a winder and wound as four cages onto a bottle. For this purpose, the chuck is rotated about its own longitudinal axis (the "chuck axis") and the thread is moved along the chuck axis with a traverse stroke approximately equal to the desired axial length of the package to be obtained. rapidly traversed in the direction.

During the formation of the thread package, the outermost layer of the thread cage is preferably held in contact over its entire length with one "contact roller", which is a friction-driven roller driven in rotation about its own longitudinal axis. The drive force is transmitted to the chuck by frictional contact with the package.

Instead of this, the contact roller can be used, for example? It may be a simple sensing roller that provides an output signal depending on the rotational speed of the chuck and is used to control a drive motor that directly drives the chuck. In either case, during the winding operation of the package, especially if friction-driven rollers are utilized,
Preferably, a controlled contact pressure is maintained between the package and the contact roller.

The winder chuck is typically cantilevered and protrudes from the front of the headstock, which contains the winder's drive mechanism and control unit. However, there is a consistent trend toward increasing the length of the chuck and increasing the size of the thread cage formed therein. At the same time, there are stiffness limits from the design of the structure of the individual chuck. Therefore, when forming the yarn arm cage, bending of the chuck as the load gradually increases is always a problem, and (7) therefore, the mother cage at the outer end tends to separate from the contact roller. be.

Such problems have been recognized for a long time and solutions have been proposed, for example, in U.S. Pat. No. 4,394,985;
No. 087055, No. 3917182, No. 3593932, No. 3042324, etc. have been proposed. However, none of these solutions is relevant to the present invention.

Means for Solving the Problems The object of the present invention is to at least alleviate the paper problems by suitably modifying the geometry of the winder.

The present invention provides an improvement in winders □ of the type with contact rollers rotatable about their own longitudinal axis ("roll axis"). The winder further includes at least one chuck rotatable about its chuck axis. The winder further includes a carrier rotatable about a predetermined "carrier axis," and the chuck is cantilevered onto the carrier. The carrier rotates about the carrier axis (8) to move the chuck relative to the contact rollers into an initial winding position where the thread is wound around the chuck. Then, the carrier rotates while moving the chuck away from the initial winding position to form a thread cage between the chuck and the contact roller.

Winding machines of the general type mentioned in the previous section are already known in the art. This example is from U.S. Patent Application No.
No. 12014 (vs. European Patent Application No. 73930 [6)].

A different type of sterilization 1, but still belonging to the type on paper, is a machine described in U.S. Patent Specification No. 4,298,171 and U.S. Patent Application No.
4483).

In the winder of the present invention, the axis of rotation of the carrier is not parallel to the axis of the contact roller. However, the chuck axis can be parallel to the contact roller axis in at least one position of the chuck relative to the contact roller during the winding operation. Preferably, this one position is an initial winding position.

In more general terms, the winding machine according to the invention comprises a contact roller rotatable about its own longitudinal axis, a chuck also rotatable about its own longitudinal axis, and chuck support means; extends cantilevered from the support means. Means are provided for determining the mode of relative movement between the support means and the contact roller, so that the chuck axis of the unloaded chuck (i.e., the chuck when it is carrying the yarn nomaque) is adjusted to the mode of relative movement between the support means and the contact roller. Only one relative position of the chuck and contact roller is substantially parallel to the contact roller axis.

In other relative positions, these axes are in a twisted relationship.

By appropriate selection of the mode of movement of the chuck when unloaded, it is possible to compensate for or compensate for the torsional behavior of the chuck due to the loads encountered during the winding operation.

<Example> Specific examples of the present invention will be explained in detail below based on the attached drawings.

For purely exemplary purposes, the present invention is based on corresponding European patent application no. 1 to 4 and 7 to 15, which are included in this issue, will be described as applied to the lower chuck of the winder described, although not shown. The disclosures of these prior applications are hereby incorporated by reference into this application.

In order to avoid unnecessary duplication and undue length of the present specification ψ(), it is assumed that the general structure of the winder and its function is already known from these earlier applications.

Wherever possible, the reference numbers used in this application shall be made to correspond to the same parts in the earlier application.

Conventional 1 Geometry" Reference numeral 18 in FIG. 3 includes a friction-driven roller mounted on the winder headstock (not shown in FIG. 1) rotatably about its own longitudinal axis 1120. Show.Axes &amp;
120 is fixed to the machine and extends substantially horizontally.

Reference numeral 26 designates a chuck mounted on a swing arm 30 as a carrier, the chuck 26 being able to rotate freely about its own longitudinal chuck axis 27.

As shown most clearly in Figure 4, the chuck 2
6 extends in a cantilevered manner from the swing arm 30 as its carrier.

The swing arm 30 is rotatably attached to the frame at a fulcrum 34 about an axis 35 fixed to the frame (not shown).

The swing arm 30 is rotatable so as to swing in an arc B on a fulcrum 34, and the chuck 26 is moved between the initial winding position shown by a solid line in FIG. 3 and the initial winding position shown by a dotted line in FIG. Move between the rest position and the rest position.

When the chuck 26 is in its rest position, the thread package carried by the chuck 26 is separated from the friction drive roller 18, thereby braking the chuck 26 and removing the thread thread or thread cage therefrom for the next It is replaced with an empty bobbin for winding operation. When the chuck 26 then moves to the initial winding position, ? The bin is in frictional contact with the friction drive roller, and the chuck 26 is caused to rotate about the chuck axis by frictional contact with the drive roller. As fully discussed in the aforementioned prior application, threads (not shown) are transferred from friction driven rollers 18 to bins, each of which is 71? The thread is wound onto the pin as a cage.

When the thread package is formed in place of the chuck 26, the chuck 26 moves from its initial winding position towards its rest position.

As shown in FIG. 4, the axes 35.20 are aligned as close to parallel as practical. Swing arm 30 relative to friction roller 18 to enable this parallel setting.
A suitable arrangement allowing adjustment of the axis of rotation of the prior application is not shown and described in FIG. 10 of the prior application. When the chuck 26 is unloaded, that is, when the chuck 26 is
Only the empty bobbin is installed, and the chuck is at its body position I.
The chuck shaft 1J27 is mounted on the swing arm 30 so that it is as parallel as possible to the axes 35 and 20 when moving from the initial winding position 1*. Thus, when swing arm 30 pivots about arc B (FIG. 3) on its fulcrum 34, axis 27 follows the arcuate path indicated at 31 in FIG. Ideally, the chuck axis should follow the same path upon return of the swing arm 30 as the chuck 26 is loaded, ie as a thread cage is formed around the chuck. However, under certain operating conditions this ideal cannot be achieved. This will become clear when considering FIG.

FIG. 5 is divided into an upper part which schematically shows certain structural elements of the chuck 26, and a lower part which schematically shows exaggerated torsions of these parts which occur during the winding operation.

The chuck structure shown in FIG. 5 corresponds to that shown in FIG. 11 of the prior application, with reference numeral 156 indicating a portion fixed to the swing arm 30 of the chuck 26, and reference numeral 184
shows a shaft attached to the chuck fixing portion 156 by first and second goal pairing units (182, 183) which are spaced apart in the axial direction. Thus, the shaft 184 and the chuck portion (
(not shown) can rotate about an axis 27. Since the chuck 26 is attached in a cantilevered manner, point E is in an unsupported state.

When the chuck 26 is unloaded or fully loaded, the shirt 184 is straight and the axis 27 extends uniformly through the pairing units 182, 183. For example, as shown in U.S. Pat. No. 4,394,984, when the chuck 26 is loaded with a long and heavy package, the axis l1li! 27 is dotted in the lower part of FIG. 5; 1c will be deformed from its own shape. The parts of the chuck within the bearing units 182 and 183 are shown in solid lines in the lower part of FIG.
It is strongly curved within the region. bearing units) 18
The shaft portion of the outer chuck of No. 2,183 is presumed to remain straight as shown by the chain line 27A in the lower portion of Fig.
Give position Ea to the free end of. In practice, the outer portion of the bearing unit of the cantilevered shaft 184 is also curved to such an extent that the chuck axis follows the lower line 278 in FIG. Therefore, the free end of the shaft 7) 184 comes to Ep. As a result, the total displacement at point E due to this load deformation is given by L, of which the contribution due to the bending of the cantilevered shaft portion on the outside of the bearing unit is t.

This results in a deformation of the ideal path 31 when the chuck 26 returns towards its rest position. The effect this has on the winding operation will be discussed later.

Geometry of the New Machine Figures 1 and 2 are diagrams of the geometry of the new B machine, greatly exaggerated for illustrative purposes. FIG. 1 corresponds to FIG. 4. That is, a side view is shown when the chuck 26 is in the initial winding position. The chuck is here represented by its axis 27 for the sake of clarity, and the friction drive roller is shown by its axis 20. Dotted line 300 represents a horizontal line passing through fulcrum 34 of swing arm 30. It is assumed that axis 20.27 is parallel to horizontal line 300. and,
The axis of rotation 35 of the swing arm 30, which moves the chuck between the rest position and the initial winding position, is inclined at an angle G with respect to the horizontal lTh 1300, as seen in this side view.

FIG. 2 is a schematic plan view of the system taken in the direction of arrow V in FIG. Therefore, FIG. 1 shows a view seen in the direction of the arrow ■ in FIG. 2. It is assumed that the horizontal 1I11300 runs parallel to the axis 20.27 in the plan view. It will be seen that the axis 35 is also set at an angle J with the horizontal line 300 in the plan view, as shown in FIGS. 1 and 2.
In both figures, the swing arm 30 is represented by a single straight line 30 extending between @1 lines 35 and 27 -
There is C. Its position with respect to these axes in FIG. 1 is of no great importance for the principle explained on the basis of these diagrams. However, hereinafter H.

Regarding the configuration and design of the equipment involved, the actual JTI f * has important meaning.

1 and 2, it is assumed that chuck 26 is in its initial winding position and is therefore substantially unloaded. The axis 27 is straight and the distance between it and the axis 20 is constant over the entire length from the swing arm 30 to the free end E of the shaft. This allows each y+e bin carried on the chuck 26 to be in at least line contact with the friction drive roller 18 over the entire length of the bin. Next, consider two virtual lines R1 and R2 that extend in the radial direction with respect to the axis 35 and connect the axis 35 and the axis 27, respectively. It is assumed that the line R1 intersects the axis 27 at a point P1 adjacent to the swing arm 30. It is assumed that the line R2 intersects the axis 27 at a point P2 adjacent to the free end E of the shaft 184. Lines R1 and R2 are axis 1! at points CI and C2, respectively.
intersects with 35.

Now, when viewed from the front, that is, in the direction of arrow ■ in Figure 1, let's consider the trajectory of points PI and P2 as the unloaded chuck moves between its rest position and initial winding position. . The diagram in Figure 6 is angle G.

This trajectory is expressed when the assumptions regarding J are changed.

In FIG. 6A, it is assumed that points CI, C2 lie in a common vertical plane and therefore angle J (FIG. 2) is zero. C2 lies above C], so the angle G (FIG. 4) is greater than zero. When the chuck 26 is in its initial winding position as shown, both PI and P2 are connected to the axis &12.
7 on a common horizontal line. The swing arm 30 rotates by an angle B (FIG. 1), returning the nayak 26 to the rest position, but only (-- the winding operation hh is not performed and the chuck remains in its unloaded state). Assume that point PI cuts segment S] in Figure 6A;
Fork point P2 cuts segment S2.

Therefore, when the chuck is in the rest position, the axis 27 is inclined with respect to the horizontal, and the point IC lies in the direction 8110 of the connection of the chuck 26 to the swing arm 30, and is substantially parallel to the axis 20 when viewed from the front. located close together. However, for this configuration (19), most of the "1 compensation displacement" (defined in the next section) appears as horizontal displacement.

For ease of identification and clarity of explanation, the term "one displacement" as used herein is shown in FIGS. 3 and 4 at an arbitrarily selected point on the chuck. It refers to the displacement or deviation of the same point in the "ideal geometry" from the "ideal path".The "displacement" caused by the deformation of the chuck due to the load is called the "deformation displacement", and The displacement is referred to as a "compensatory displacement" or "one compensatory displacement".

Referring to Figure 6B, consider the case where it is assumed that the points CI, C2 lie in the horizontal plane, i.e. the angle G in Figure 1 is zero, but the angle J (Figure 5) is greater than zero. Let's try it. Most of the compensation displacement of the axis 27 appears as a vertical displacement, and in the rest position point E lies substantially higher than in the region of the connection of the chuck 26 to the swing arm 30.

Figure 6C shows the geo (
20) Show metrics. The angle is chosen for demonstration purposes only and has no real meaning.

Robbery! The vertical component of the compensatory displacement of the dot during the movement through the arc 81.82 of points PI and P2 in FIG. 6 acts to compensate for the deformation of the chuck due to static loads during the winding operation. I believe that you can understand.

As clearly shown in FIG. 5, the static load on the chuck caused by the increase in weight 1 during package formation is at point E relative to the chuck's connection to the swing arm 30.
has a tendency to push down. However, the compensating displacement referred to in the discussion of FIG. 6 has a tendency to lift point E relative to the connection of the chuck to the swing arm. By suitably selecting the machine geometry, taking into account the design conditions of the machine and the specific construction of the left and right through-hole cages and chucks, it is possible to compensate for at least some of the chuck deformations that occur during the winding operation.

- As can be seen, the horizontal compensation displacement of points PI, P2 in FIG. 6 introduces additional errors in this system. However, even if this interpretation is correct, the overall error when adopting the new geometry will be significantly smaller than the corresponding error introduced by static loads in the winding system using the standard geometry of the prior art. be able to. Furthermore, this horizontal compensating displacement has been found to be advantageous in the illustrated embodiment, i.e. in the illustrated embodiment type, the yarn is
Winding area 2 transferred from to the cage (Fig. 6A)
intersects a horizontal plane containing the axis 20 of the drive roller and is defined by a small circular arc on the outer circumference of the drive roller.

In such a configuration, a horizontal compensating displacement toward axis 20 at point E (FIG. 6A) tends to keep the outer end package driven into contact with friction roller 18. Therefore, this one theoretical error has a beneficial effect in practice.

Furthermore, this system can be designed such that the horizontal component of the compensating displacement of points PI, P2 has a one-dimensional "compensating effect. For example, the chuck is aligned with the friction roller when approaching the initial winding position rt. Instead of making contact, it may be configured to make point contact first at a point adjacent to the outer end of the chuck, that is, at a point adjacent to point EK. An additional force can be applied to the arm 30 and a prestress can be applied to the chuck. This requires a horizontal movement of point E relative to the connection between the chuck and the swing arm. can be easily designed to absorb such prestresses, which may be due to the excessive pressure required to ensure parallelism of the axes 20 and 27 when the chuck is in the initial winding position. This can be minimized by designing the friction roller 18 to deform slightly in response to the winding operation.
The horizontal component of the compensation displacement can be made to at least partially balance the angular initial setting of the chuck axis, so that a relatively soft cage (as in FIG. 6B) can be used. As the pressure builds up between the chuck and the friction roller, the excessive pressure decreases or disappears.

Practical Embodiment Referring to FIG. 7, the swing arm for the lower chuck of the winder can be mounted to effect the desired movement of the chuck. Figure 7 of the present system shows the lower chuck of such a machine, but the basic principle is the same for both the upper and lower chucks. Minor differences in the application of these principles to the upper and lower chucks, respectively, will be explained later.

Reference numerals 130 and 132 indicate the load bearing/4'-tision of the headstock of the machine shown in FIG. 8 of the prior application. In particular, the swing arm is indicated at 30 and extends radially from a support shaft 34 which is supported between the partitions 130 and 132 by a bearing system to be described below. The swing arm 30 has a fixed portion 156 of the chuck 26 (
(See also Figure 3) Gripping Cranzo jaws 154A, 154
It has B. In prior application No. 412014, the chuck axis is, for example, axis 3 as shown by dotted line 270.
M-1 to hold the chuck so that it is parallel to 5.
The temperature was 54°C. -15 shown in Figure 7
4A and 15/JB are configured to hold the chuck so that the chuck axis 27 is inclined to the line 270. In the figure, only the inclination within one plane is shown, but the inclination is also shown in the horizontal plane perpendicular to the plane of the figure.]
-I can do something. The slope to be provided in each case will be explained later.

i'? - One bearing unit 140 attached to the tipion 130 has a partially spherical outer race 139; Attach the support shaft 34 to 9-132.
The other bearing unit 142 attached to the partition 132 has a smaller size than the receiving opening 143Vc of the partition 132, and passes through the flange 144 and the enlarged opening (not shown) of the version 132.
5 is held at the node 132. This configuration allows the support shaft 34 to be adjusted to a desired position within an "adjustment cone" whose apex is a point C within the bearing unit 140.

A friction drive roller 18 can also be mounted to these load bearing partitions 130, 132 such that its axis 20 extends in a predetermined arrangement relative to these partitions. When the chuck and swing arm are assembled as shown in FIG. 7, the swing arm 30 can be pivoted to bring the chuck 26 into contact with the friction drive roller. The bearing for the support shaft 34 can then be adjusted to bring the chuck axis 27 into the desired alignment relative to the roller axis 20. At this time, the chuck 26 and the friction roller 18 come into line contact without applying excessive pressure to the swing arm 30,
Alternatively, the axis 27 may be placed at a slight angle to the axis 20 and the overpressure described above is required to force the chuck into the initial winding position where line contact is achieved.

For ease of identification and simplicity of explanation, the displacement or inclination of the chuck axis 27 from line 270 (FIG. 7) will hereinafter be referred to as the "cant" of the chuck axis, and will refer to the "cant" of the chuck axis when the chuck axis is in the initial winding position. Swing arm axis 35 to return
The corresponding adjustment of is called the "tilt" of the carrier axis.

Choosing Appropriate Geometry - Preliminary Now consider again the diagram in the lower part of FIG. If the cantilevered shaft part 1 of the chuck
If 84 has relatively high rigidity against bending load, then
Dimension l is a really small portion of dimension L. Therefore, in order to compensate for bending of the chuck, it is sufficient to compensate for the deformation displacement of a point such as point E at the free end of the chuck. Compensation errors along the entire length of the chuck are small and can be ignored.

On the other hand, if the cantilevered shaft portion 18 of the chuck
4 bends considerably under the expected load, the dimension t will account for a significant proportion of the dimension L, and compensation with reference to point E will not be sufficient. In this case, a point near the inner end of the chuck (27) is chosen to provide an averaged compensation along the entire length of the chuck.

Wherever the compensation point is chosen, it is usually undesirable to rely on one calculation of the deformation displacement of the compensation point from the ideal path. This is because the total deformation displacement across the compensation point depends on the structure of the chuck. Not only because it depends, but also because the degree to which it becomes
This is also because this deformation displacement depends on the overall design of the machine, and the considerable influence of equivalent displacements can be expected at least from the design of the swing arm and its support structure.

Therefore, it is usually preferable to measure the deformation displacement by 6".

Since this displacement is caused by a static load under the weight of the package, such measurements can be easily made by applying an equivalent load to the chuck while the machine is not running. . As a means for this purpose, the diagram shown in FIG. 8 is prepared, for example. FIG. 8 shows the expected deformation displacement of the compensation point from the ideal path under given operating conditions.

In FIG. 8, the ideal path is indicated by 310 (28) and the expected path along the compensation point when the chuck is not compensated is indicated by 312. Reason ff
The jJ path is the path of the selected compensation point when the chuck is not loaded. The expected actual path may vary: a series of measurements representing the downward displacement of the compensation point when different static loads are applied to the chuck (in Figure 8, the two paths are connected). (indicated by the vertical line) can be generated from the ideal path by taking These different static loads are associated with the weightage formed at various stages during the winding operation and thus at specific positions of the chuck along the ideal path.

It can be related.

Therefore, the problem of selecting a suitable winder geometry is
As mentioned above, the problem comes down to matching the compensation effect that can be obtained from the [new geon having the deformation displacement diagram obtained in step 7].

As is clear from the above discussion, the task of matching does not necessarily mean making the compensated path as close as possible to the ideal path, but rather that the best compromise for the actual intended operating conditions is determined in each case. must be accepted.

Given the large number of factors that influence the choice of geometry in each individual case, it is pointless to provide fixed principles for the selection of winder geometry in this specification. Instead, various ways of approaching the selection of a particular winder geometry are presented below.

However, these approaches are not exhaustive.

Considering FIGS. 6A and 6B, it can be seen that the system can be configured such that the compensation effect is purely vertical at the angular position of the swing arm 30. One approach to matching the compensation effect therefore consists in specifying this purely vertical compensation relative to the oscillating motion of the swing arm 30 in the actual winder design. Using the diagram in Figure 6, as shown in Figure 6D,
This is the point PI after being rotated by the same angle B8 with the rotation of the axis ffM350 (which is inclined with respect to the plane of the paper),
It comes down to the problem of identifying the position where P2 reaches the position where they line up vertically. At the same time, the degree of compensation must be appropriate to the expected deformation of the chuck. Such problems can be conveniently submitted to computer analysis.

Figure 9 shows another approach, which is suitable for conventional graphical solutions. As is clear from the foregoing description, this figure also illustrates the further substantial improvements that can be obtained with the present invention. For convenience,
This figure assumes a point Ek at the confession end of the chuck. However, the same principle is applicable to any selected compensation point.

In FIG. 9, a curve (not shown) connecting points EO to EO represents the ideal path of point E during the winding operation, that is, when the yarn is being wound onto a package carried by the chuck. E
O marks the initial winding position and EO is where the winding operation is interrupted and the completed yarn package is removed from driving contact with the drive rollers. In is the radius extending to the (31) center of this ideal path.

Line T shows the position of the unloaded canted chuck axis (27 in FIG. 7) relative to radius RK when viewed in the axial direction of the friction drive roller. Lines X and Y are the initial winding position E
The horizontal component of the tilt applied to the swing arm and the chuck carried thereon (e.g., by adjustment of bearing unit 142 with reference to FIG. 7 above) to return the chuck to a horizontal configuration at Indicates the vertical component.

Lines D1 to D6 show the compensation displacements required to balance the deformation of the chuck due to static loads during a particular winding operation (indicated by the deformation displacement at point E) at points E1 to EO, respectively. .

These lines are simply the reversal of the deformation displacements shown in FIG. Assume here that it is desired to compensate the deformation displacement of point E as closely as possible at the completion of the winding operation, ie at position E6. Then, the effect of the cant of the chuck on the swing arm (indicated by IJT in Fig. 9) and the effect of the tilt (32) of the swing axis of the swing arm (indicated by the horizontal component X and the vertical component Y in Fig. 9) ) must exactly cancel the corresponding deformation of the chuck (indicated by line D6 in FIG. 9), ie line T.

It is necessary that X, Y, and D6 form a closed figure.

Achieving such a result results in the following two steps.

1) Choose angles α and β such that the compensation effect is purely vertical at EO.

2) Adjusting the chuck axis in the plane X-X (the plane perpendicular to the paper and containing line T) so that the vertical compensation effect at point E6 exactly balances the chuck deformation at the same point.

Step 1 Having learned the geometry of Figure 9, the desired vertical component of the compensation effect at point E6 is the angle α (α is tan α = Y/X
) is approximately half the swing angle of radius H between points EO and EO. The angle β is an independent variable and any desired practical value can be chosen.

The selection of angles α and β for this compensation technique is based on the plane in which the adjustment (cant) of the chuck axis relative to the swing arm is to be performed (indicated by
Includes the selection of At the same time, it is necessary for the mounting of the swing arm to have an opposing adjustment ( represents the selection of parallel planes on which tilting is to be performed. The magnitude of the adjustment still has to be determined and this is handled in step 2 below.

In practice, the free end of the chuck should be adjusted towards the friction roller such that the angle α+β represents the angle between the radius R at point KO and the horizontal line at that point. Since the angle β has no effect on the desired compensation, the placement of R at the EO can be determined by mechanical design factors other than the proposed compensation technique, and is given for the purpose of that technique. can be accepted as such. For a given length of the swingarm, the swing angle of the swingarm depends only on the size of the cage. Therefore, angle α is an equivalent control variable.

The following two additional considerations are of value in terms of seedling yield.

a) Of the total angle of oscillation of the swing arm 30, that part is really important for compensation purposes, the part that is relevant for the actual mid-cage winding. The part of the swing path between the winding stop position and the rest position can be ignored.

b) Is there a theoretically usable area for purely vertical compensation? It is not essential that this occurs in the part of the rocking path associated with cage formation or in the rocking path defined by the machine. The setting of this area at a specific position in the "oscillation path" is taken as an example of a possible matching operation; other matching operations using other % edges can be adapted to suit individual requirements. Step 2 Assuming that the angles α, β are selected (35) to match the predetermined operating environment, step 2 as outlined above is taken up. Closed figure T in FIG.

At Y, Probably. This allows calculation or measurement of the corresponding length n along the line T suitable for creating the desired closed figure.

Consider now the plane xx shown in FIG. 9 and shown (on a reduced scale) in FIG. 10. In Figure 10,
Line 3]4 represents the chuck axis arrangement of the theoretically ideal model shown in FIGS. 3 and 4. 1316 after being canted relative to the swing arm on the same axis (around a point Q located somewhere on the chuck mount, see Figure 7), and when the swing arm moves along the chuck axis E.
The configuration is shown before it is tilted back to a horizontal configuration at 0. The length of the chuck is given by N. This is the 9th
Although it should be drawn on a scale that adopts the representation of the predetermined compensation displacement D6 in the figure, it has been reduced considerably (36) in FIG. The value n actually measured in FIG. 9 is the vertical spacing between the ends of the chuck in the canted position in FIG. 10, and the length n and N are the required adjustment angle θ.
give.

The required tilt of the swing arm is also given by the angle θ, and this tilt of the swing arm must be carried out in a plane parallel to the plane X-X. In practice, there is no need to identify the plane or the magnitude of the swing arm's tilt; the swing arm is
It is simply tilted to negate the effect of cant on.

The geometry of the system is thus formed and the errors as a result contained in positions E1 to E5 can be estimated as shown in FIG. 9, and these errors are respectively i1i! Represented by F1 to F5. E
The magnitude of the error in l is substantially equal to the magnitude of the chuck deformation at this location, and there is no hope of improvement at this stage of the winding operation. On the other hand, the magnitude of the deformation is anyway small and tolerable at this stage. As the winding operation progresses from stage E2 to E5, the weight of the package increases, and the very large improvement obtained by the present invention shows that the respective errors F2 to F5 with respect to compensation displacements D2 to D5 are comparatively This is confirmed by At point E6, an error of zero is theoretically obtained despite the fact that the deformation of the chuck is very large at this stage of winding.

11 Lower Margin Modification As an example, the present invention has been described above with reference to the lower chuck of the Evening/Eve automatic winding J1!2 machine shown in U.S. Patent No. 412,014. The present invention can also be effectively applied to correction of chuck deformation of the upper chuck of such a winder during winding operation. However, in this 1st case, the electric field of ノ and tsage and the cha that causes its condensation,
Since the deformation of the chuck will cause the free end of the chuck to move downwardly into contact with the friction drive roller, it is preferable to incorporate small, prudent errors into the compensation path of the chuck. In such a case, it is best to avoid excessive compensation, and therefore, if there is an error, it is preferable that the error is on the under-compensation side.

It is quite obvious that the invention is applicable to winders having a chuck, in which the chuck has a swinging arm swinging from either above or below the friction-driven roller. carried by. It will be clear that the present invention is applicable to other types of automatic winders, such as the known glue-type winders as shown in U.S. Pat. No. 4,298,171. In such a winder, it can be seen that the cant of the chuck relative to the swing arm of the embodiment described above is equivalent to the cant of the chuck axis 318 (FIG. 11) relative to the rippler head 320 (FIG. 11); It can be seen that the tilt of the swing arm at its attachment point is equivalent to the tilt of the rotation axis 322 (FIG. 11) of the male bar head itself. Since the principles applied in this type are the same as in the embodiments described above, it is not considered necessary to describe the embodiments of the rippler head winder in further detail.

The present invention is also at least theoretically applicable to machines such as those shown in U.S. Pat. No. 4,394,985, in which the movement of the chuck from the rest position to the initial winding position does not involve rotational movement. It is. In such a case, instead of (or in addition to) providing a force applying means for pressing the cage against the friction drive roller, in the embodiment of the above patent, A variant can be configured such that the id hand 1, which defines the path of movement of the gear ridge supporting the chuck, defines a curved path for the carriage. By appropriately adopting this curved motion path, the above rotating fruit m 13'! The compensation effect explained in Section I is one of them.
It can also be obtained in the case of the η line example. However, economically producing such an id system may be problematic.

In the embodiments described above, a preferred arrangement was used in which the winding area 2 (FIG. 6A) is arranged in a horizontal direction passing through the axis of the friction drive roller. This is not necessarily the basic 6-winding vA1 or friction driven row 2 from this proper arrangement.
can be moved toward a position about the vertical plane in a vertical plane containing the axis of the vertical plane. However, the effectiveness of the available compensation decreases as the winding area is moved vertically.

The invention is not limited to the details of the swing arm and mounting structure described with reference to FIG. Many winding configurations can be employed in accordance with the present invention, as illustrated by the Hini dP Le 9-type embodiment. However, FIG. 7 emphasizes that the present invention can be applied to existing winding structures with slight modifications.

It should first be emphasized that the deformation displacements that have to be compensated for according to the invention are very small. For the sake of clarity, these displacements are greatly exaggerated in the drawings of this specification. for example,
In view of the properties of the package described below, the deformation which produces a displacement from the ideal path at the free end of the winder's wheel has a small value of 1 to 2 mm in practice.

The most obvious event of chuck deformation in an uncompensated system is when the saddle (5add
le ) become visible.

When viewed in longitudinal section, such a mother, Cage, has raised shoulders, and a depression is formed between her eyebrows. A well-known and relevant occurrence in the use of such machines is: - Variations in the hardness of the arm cage. Due to the deformation of the chuck, most of the contact pressure between the cage and the friction drive roller is generated by the holes on the inner end side. They are thereby solidified and hardened, IA=
It is harder than the iR package on the green side. A further disadvantage without compensation is the variation in the diameter of the flat cage along the chuck for a given winding operation, with the diameter gradually increasing towards the outer end of the chuck. Additionally, the outer package in some cases has a substantially conical profile.

By selecting a suitable compensation curve in conjunction with the measured deformation curve (FIG. 8), the above-mentioned disadvantages can in many cases be considerably reduced.

The theoretical analysis depicted in FIG. 12 can lead to formulas used to match new geometries to specific practical requirements.

In Fig. 12, the radius R is the same as the radius shown in Fig. 9, and the quarter-circle locus is drawn through the points corresponding to gO, El, etc. in Fig. 9. be. The starting point EO is shown in the upper part of this curve.

Point Er is an arbitrarily selected point on this curve corresponding to an arbitrary swing angle φ. A Cartesian coordinate system with the origin at Er is assumed, with the vertical Y-axis and horizontal X-axis shown in dotted lines in FIG. Angle 4 is the angle between the horizontal X-axis and radius R at an arbitrarily selected point Er.

The line T1 angles α, β in FIG. 12 correspond to the similarly represented elements in FIG. 9, and the length n in FIG. 12 is the length n described with reference to FIGS. has the same meaning as

Point Ee is the corrected position corresponding to the swing angle φ.

This is obtained by the method described with reference to FIG.

Line V can be called a compensation vector representing the difference between the ideal geometry of FIG. 1 and the newly compensated geometry.

The coordinates of point Ea are given as follows.

X (Ec) = n cOs (βt4) - n cos
αY (Ea) = n sln (β→-4) tenn5
lnα Considering a triangle formed by a 1m straight dotted line parallel to the Y axis, (β+4)=(φ−α).

According to the standard square law of triangles, V” = X2+Y2-4 n2sin2φ2, i.e.
Further, using the same formula, we obtain the following equation: V=2nsinφ.

φ−2α Tan Angle r =Y7'X=-cot2wT
an (90+φ−α) φ, i.e. the angle γ−90+i−α These relations are suitable for any arbitrarily chosen point Er, and they represent the compensation function in terms of n, α, φ. For a given practical application, assuming that the desired compensation is known for various values of φ (e.g. by measuring the deformation of the sandal as described above), matching the compensation function various values, nla
This can be done by selecting .

Practical Example For purposes of illustration only, the following data regarding a practical winder is provided. This data pertains to the lower chuck of the winder according to Figures 8 to 12 of prior U.S. patent application Ser. It is something that This data is based on a given winding operation (filament type,
number of packages, etc.), but such details do not seem relevant to the example.

/4' Maximum diameter of cage 360 angle α (Fig. 9) 18.5° angle β (Fig. 9) 36° long (Fig. 9, 10) 3 m + angle θ (Fig. 10) 0.19° FIG. 13 shows the means by which a predetermined setting (cant) for the chuck of the swing arm can actually be produced. This figure shows the swing arm 30 and the nozzles 154A and 154B (the latter only partially visible) as seen in the direction of arrow X111 in FIG. 7, and the characters are omitted.

The circle m formed in 154A is indicated by 155, and the trailing edge or rim of the cylinder yjr formed in 154B is indicated by 157.

The center of leading edge 155 is indicated at 300 and the center of trailing edge 157 is indicated at 302. Zom154A.

A cylindrical bore at 154B is drilled on a common axis connecting centers 300 and 302. The required offset of these centers can be determined with reference to the compensation geometry and component dimensions described above. This offset determines the cant mentioned above, and the angle β (FIG. 9) connects the center 300.302 (as seen in FIG. 13) with the axis 35.
(FIG. 7).

Such a system produces a cant of the chuck that is fixed relative to its arm. Alternatively, a pair of interchangeable liners for each di-four! , a shell can be inserted, and a pair of E holes are drilled on a common axis, but each pair has a different hole, corresponding to the center 300, 302 of FIG. The center of the offset is (49).

do. So the cant can be changed by selecting different pairs of bushes.

Alternatively, each jig may have an adjustable setting element, such as a screw, to hold the jig in a selectively variable position relative to the jig. moreover,
Each jig has a pair of juxtapositions that are adjustable and retainable relative to each other so that together with the chuck they can form a universal joint (with limited v!4 moderation).

The above discussion assumed that the new geometry was achieved by adjusting the chuck axis and carrier (swing arm) axis relative to a fixed horizontal contact (friction) roller axis.

This does not necessarily have to be the case.

In practice, if a horizontal carrier axis tilt is not possible (
For example 1. Existing glue? (which may occur when incorporating the system according to the invention into a Rupertiger winder), the contact roller axis may be tilted in order to obtain the desired relationship between the chuck and the contact roller in the initial winding position. Basically (5Q). Alternatively, the chill j- can be divided and coexisted on the contact roller axis and the swing arm axis.

This is likely to introduce a further complicating factor into the matching process. This complexity can be identified by further consideration of Figures 9 and 12 and the assumptions contained in these figures. Each figure represents the geometry of the system in a plane perpendicular to the chuck axis at the compensation point E. This plane is called the compensation plane (corresponding to the compensation point) and is not to be confused with the accommodation plane X-X mentioned above. Now, if the chuck axis is horizontal at the initial winding position, it is vertical throughout the ideal geometry before compensation.

Let us now consider the modified diagram N shown in Figure 8.

This represents the deformation within the 4 m orthogonal plane (deformation plane) at the compensation point E. Therefore, when the chuck axis is horizontal in the initial winding position, the compensation plane and the deformation plane are equal. However, when the axis of the contact roller is tilted so that the chuck axis in the initial winding position is correspondingly inclined with respect to the horizontal, the compensation plane and the deformation plane are no longer equal. This is because the deformation plane is always vertical. For small tilt angles, the complexity is negligible. For accurate matching, the problem can be solved by mapping the compensation function onto the deformation plane or by massaging the deformation function onto the compensation plane. Matching techniques other than those described above are equally acceptable. One solution is to measure the apparent deformation of the chuck by looking at the chuck in the direction of the chuck axis. It will be appreciated that where a tilt is applied in the carrier axis and the contact roller axis is tilted relative to the horizontal, corresponding steps are required.

In the movable contact roller package drive system, the axis of rotation of the chuck carrying the package is held stationary during the winding operation, and the contact rollers are moved to i'? for package formation. Many of them are movable relative to the cage. Such movement is generally performed by a linearly movable roller-carrying slide (eg, US Pat. No. 3,999,755). The present invention is also applicable to such systems in U.S. Pat.
Using a system similar to that shown in No. 4,394,985, i.e. CM mA-like slider no. It is possible to proceed by providing a curved id means on the id. 4
The same is true in both cases regarding the issue of tight manufacturing.

Such a system violates U.S. Fraud No. 408 in that:
It will be different from 7055-@. That is, the slide 9 movement and the deformable capture system are combined into an integrated machine geometry.

U.S. special issue No. 14087055? In some cases, these systems are separate.

The invention provides that the axis of the contact roller is excited relative to the contact ruler by the movement of the chuck carrier, which is capable of swinging on an axis that remains stationary throughout the winding operation.
It can be most easily applied to systems designed to

Extent of Compensation As mentioned above, there is a possibility of undercompensating the system if the deformation tends to force the chuck into contact with the contact roller. It should be understood that it is preferable to overcompensate the system in cases where the deformation tends to pull the chuck away from the contact roller (as in FIG. 9, for example). The best compromise is a mixture of over- and under-compensation, with less compensation occurring during the early stages of the winding operation. For example, where the deformation tends to pull the chuck away from the contact roller, the system will be undercompensated in the early stages of the winding operation and overcompensated in the later stages.

Move the breastless chuck of the chain towards or from the initial winding position.
When the chuck and the contact row 2 first make local contact (point contact) with each other, the means for moving the row 2 is used to apply force so that the row 5 is parallel to the initial winding position.
It can also be used. A suitable upper Me means (piston and cylinder unit) for a swing arm winding bin is shown in US Pat. No. 4,120,14. vinegar? Appropriate installation of two sets of winding machines (piston and cylinder unit with drive transmission gear system)
is shown in US Pat. No. 4,298,171. Other chuck movement systems can also be used. Systems in which rollers are moved relative to a fixed chuck are also well known, for example from US Pat. No. 3,575,357.

[Brief explanation of the drawing]

1 and 2 are a side view and a plan view, respectively, showing an exaggerated geometry of a winder according to the present invention, and FIGS. 3 and 4 are front views, respectively, showing an ideal geometry according to the prior art. and a side view, FIG. 5 is a schematic diagram showing the deformations that occur in the ideal geometry of FIG. 2, FIGS. 6A to 6D.
7 is a plan view of the swing arm of the winder according to the invention, and FIGS. 11 is a side view of another type of machine to which the invention is applicable; FIG. 12 shows the new geometry; FIG. 13 is a side view of one end of the swing arm of the winder according to the present invention. 18... Friction drive roller, 20... Roller axis, 2
6... Chuck, 27... Chuck axis, 30...
・Swing arm, 35...Arm axis line. Patent applicant MaschinenfupurikrieterakchenrSellschaft Patent agent Akira Aoki Patent attorney Kazuyuki Nishidate Patent attorney Kyosuke Nakayama Patent attorney Akira Yamaguchi ° Masaya Nishiyama [Katana] 10〕 q〕 1 − q〕 01 Bite ψ j1 ``

Claims (1)

[Scope of Claims] 1. A contact roller rotatable about a longitudinal roller axis, at least one chuck, and a carrier member rotatably supporting the chuck about a longitudinal chuck axis. the carrier member is rotatable about a predetermined carrier rotation axis for moving the chuck toward and away from the initial winding position; the winder, the axis being arranged such that the carrier rotation axis is not parallel to the roller axis and the chuck axis can be arranged parallel to the roller axis in at least one position of the chuck; . 2. The winding machine according to claim 1, wherein the moyariya member is a swing arm. 3. (1) The soft winding machine according to claim 1, characterized in that the carrier member υ is a rubber head. 4. Front 1; Place the contact roller in the fixed position of the winding machine with its roller 11 (11.! I
A winding machine according to claim 1, which has an H characteristic. 5. The roller axis is substantially horizontal. 1'FfClaim 11V
轡. 6. The winding machine according to claim 1, wherein the chuck axis is parallel to the roller axis at the initial winding position. 7. A suppressing means is provided for pushing the front N picchuck into contact with the contact roller, and the chuck moves along a path such that the chuck makes local contact with the contact roller. 2. The winding machine according to claim 1, wherein the suppressing means is configured to suppress the chuck and the contact roller so that they become parallel to each other. 8. a contact roller having a longitudinal roller axis, at least one chuck, support means for cantilevering said chuck, and controlling the mode of relative movement between said support means and said contact roller under no load. means for defining the chuck axis of the chuck to be substantially parallel to the roller axis in only one relative position therebetween. 9. The winder according to claim 8, wherein the contact roller is mounted with its roller axis at a fixed position on the winder. 10. The winder according to claim 8, wherein the roller axis is substantially horizontal. 11. The winding machine according to claim 8, wherein the chuck axis is parallel to the roller axis at the initial winding position. 12. Repression means are provided for pushing the chuck into contact with the contact roller, the chuck being movable along a path such that the chuck is brought into local contact with the contact roller; 9. The winding machine according to claim 8, wherein means is adapted to suppress the chuck and the contact roller so that they are parallel to each other. 13. A contact roller rotatably mounted at a juncture of a longitudinal roller axis, and at least one chuck mounted rotatably at a 11!1 rotation of a longitudinal chuck axis. 1. The chuck is movable between a rest position spaced from the contact roller and a take-up position adjacent the contact roller for receiving and winding the yarn, and the chuck axis is in the take-up position. a thread nozzle disposed parallel to said roller axis at said position and comprising means for moving said front H1:1 chuck between said positions such that said chuck axis is not parallel to said roller axis during such movement; Winding machine for f-cage. 14. Is via 1 the means for moving the chuck? Claim 13JJi further comprising an extended arm pivotable about a pivot axis, the chuck being mounted to the arm in a spaced relationship from the pivot axis. The winding machine described. 15. a contact roller rotatably mounted about a longitudinal roller axis; at least one chuck rotatably mounted about a longitudinal chuck axis; and at least one of said contact roller and said roller. one of which is moved relative to each other so that when the contact roller and the chuck are in the initial winding position, the roller axis and the chuck axis are positioned in a parallel relationship with each other, and the contact roller and the chuck are in the initial winding position. and means for positioning the yarn packages out of parallel relationship with each other when spaced apart from the take-up position. 16. Said means are coupled to said chuck for moving said chuck between said initial winding position and a rest position spaced from said contact roller. The winding machine described. 17. The winder of claim 15, wherein said means is coupled to said contact roller for moving said contact roller away from said initial winding position and said chuck. 18. a contact roller rotatable about a longitudinal roller axis; at least one chuck; and a carrier member rotatably supporting the chuck about a longitudinal chuck axis; The carrier member is rotatable about a predetermined carrier rotational axis for moving the chuck toward and away from an initial winding position, the carrier rotational axis and the chuck axis being Winding machines characterized in that they are arranged out of parallel to each other. 19. The winding machine according to claim 18, wherein the chuck axis can be arranged parallel to the roller axis at the initial winding position. 20. Winding machine according to claim 19, characterized in that the chuck is brought into local contact with the contact roller when it is moved to the initial winding position.